Rocker shaft mounted engine brake

ABSTRACT

A system for actuating an engine valve is disclosed. The system may include a lost motion housing having two spaced collars surrounding a rocker shaft. The lost motion housing may include an internal hydraulic circuit connecting a hydraulic fluid supply passage with an actuator piston. The system may include a means for securing the lost motion housing in a fixed position relative to the rocker shaft.

CROSS-REFERENCE TO RELATED APPLICATIONS

The present application relates to, is a continuation in part of, andclaims the priority of U.S. patent application Ser. No. 12/076,173 filedMar. 14, 2008 entitled “Engine Brake Having An Articulated Rocker ArmAnd A Rocker Shaft Mounted Housing,” which relates to, and claims thepriority of U.S. Provisional Patent Application Ser. No. 60/895,318filed Mar. 16, 2007, which is entitled “Engine Brake Having anarticulated Rocker Arm and a Rocker Shaft Mount Housing.”

FIELD OF THE INVENTION

The present invention relates to a system and method for providingengine braking in an internal combustion engine.

BACKGROUND OF THE INVENTION

Internal combustion engines typically use either a mechanical,electrical, or hydro-mechanical valve actuation system to actuate theengine valves. These systems may include a combination of camshafts,rocker arms and push rods that are driven by the engine's crankshaftrotation. When a camshaft is used to actuate the engine valves, thetiming of the valve actuation may be fixed by the size and location ofthe lobes on the camshaft.

For each 360 degree rotation of the camshaft, the engine completes afull cycle made up of four strokes (i.e., expansion, exhaust, intake,and compression). Both the intake and exhaust valves may be closed, andremain closed, during most of the expansion stroke wherein the piston istraveling away from the cylinder head (i.e., the volume between thecylinder head and the piston head is increasing). During positive poweroperation, fuel is burned during the expansion stroke and positive poweris delivered by the engine. The expansion stroke ends at the bottom deadcenter point, at which time the piston reverses direction and theexhaust valve may be opened for a main exhaust event. A lobe on thecamshaft may be synchronized to open the exhaust valve for the mainexhaust event as the piston travels upward and forces combustion gasesout of the cylinder. Near the end of the exhaust stroke, another lobe onthe camshaft may open the intake valve for the main intake event atwhich time the piston travels away from the cylinder head. The intakevalve closes and the intake stroke ends when the piston is near bottomdead center. Both the intake and exhaust valves are closed as the pistonagain travels upward for the compression stroke.

The above-referenced main intake and main exhaust valve events arerequired for positive power operation of an internal combustion engine.Additional auxiliary valve events, while not required, may be desirable.For example, it may be desirable to actuate the intake and/or exhaustvalves during positive power or other engine operation modes forcompression-release engine braking, bleeder engine braking, exhaust gasrecirculation (EGR), or brake gas recirculation (BGR). FIG. 19 ofco-pending application Ser. No. 11/123,063 filed May 6, 2005, which ishereby incorporated by reference, illustrates examples of a main exhaustevent 600, and auxiliary valve events, such as a compression-releaseengine braking event 610, bleeder engine braking event 620, exhaust gasrecirculation event 630, and brake gas recirculation event 640, whichmay be carried out by an exhaust valve using various embodiments of thepresent invention to actuate exhaust valves for main and auxiliary valveevents.

With respect to auxiliary valve events, flow control of exhaust gasthrough an internal combustion engine has been used in order to providevehicle engine braking. Generally, engine braking systems may controlthe flow of exhaust gas to incorporate the principles ofcompression-release type braking, exhaust gas recirculation, exhaustpressure regulation, full cycle bleeder and/or partial bleeder typebraking.

During compression-release type engine braking, the exhaust valves maybe selectively opened to convert, at least temporarily, a powerproducing internal combustion engine into a power absorbing aircompressor. As a piston travels upward during its compression stroke,the gases that are trapped in the cylinder may be compressed. Thecompressed gases may oppose the upward motion of the piston. As thepiston approaches the top dead center (TDC) position, at least oneexhaust valve may be opened to release the compressed gases in thecylinder to the exhaust manifold, preventing the energy stored in thecompressed gases from being returned to the engine on the subsequentexpansion down-stroke. In doing so, the engine may develop retardingpower to help slow the vehicle down. An example of a prior artcompression release engine brake is provided by the disclosure of theCummins, U.S. Pat. No. 3,220,392 (November 1965), which is herebyincorporated by reference.

During bleeder type engine braking, in addition to, and/or in place of,the main exhaust valve event, which occurs during the exhaust stroke ofthe piston, the exhaust valve(s) may be held slightly open duringremaining three engine cycles (full-cycle bleeder brake) or during aportion of the remaining three engine cycles (partial-cycle bleederbrake). The bleeding of cylinder gases in and out of the cylinder mayact to retard the engine. Usually, the initial opening of the brakingvalve(s) in a bleeder braking operation is in advance of the compressionTDC (i.e., early valve actuation) and then lift is held constant for aperiod of time. As such, a bleeder type engine brake may require lowerforce to actuate the valve(s) due to early valve actuation, and generateless noise due to continuous bleeding instead of the rapid blow-down ofa compression-release type brake.

Exhaust gas recirculation (EGR) systems may allow a portion of theexhaust gases to flow back into the engine cylinder during positivepower operation. EGR may be used to reduce the amount of NO_(x) createdby the engine during positive power operations. An EGR system can alsobe used to control the pressure and temperature in the exhaust manifoldand engine cylinder during engine braking cycles. Generally, there aretwo types of EGR systems, internal and external. External EGR systemsrecirculate exhaust gases back into the engine cylinder through anintake valve(s). Internal EGR systems recirculate exhaust gases backinto the engine cylinder through an exhaust valve(s). Embodiments of thepresent invention primarily concern internal EGR systems.

Brake gas recirculation (BGR) systems may allow a portion of the exhaustgases to flow back into the engine cylinder during engine brakingoperation. Recirculation of exhaust gases back into the engine cylinderduring the intake and/or early compression stroke, for example, mayincrease the mass of gases in the cylinder that are available forcompression-release braking. As a result, BGR may increase the brakingeffect realized from the braking event.

SUMMARY OF THE INVENTION

Applicants have developed an innovative system for actuating an enginevalve comprising: a rocker shaft having a hydraulic fluid supplypassage; a lost motion housing having a collar surrounding the rockershaft, an actuator piston bore, and an internal hydraulic circuitextending from the actuator piston bore to the hydraulic fluid supplypassage; means for securing the lost motion housing in a fixed positionrelative to the rocker shaft; and an actuator piston slidably disposedin the actuator piston bore. In the foregoing system, the hydraulicfluid supply passage extends internally through the rocker shaft.Further, the lost motion housing may have two collars surrounding therocker shaft. Still further, a control valve bore may be provided in thelost motion housing, wherein said control valve bore communicates withthe internal hydraulic circuit and a control valve is disposed in thecontrol valve bore. Still further, a check valve may be disposed in thecontrol valve. Still further, the means for securing may be provided ona side of the lost motion housing which is distal from the actuatorpiston, on a side of the lost motion housing which is proximal to theactuator piston, or on both the side of the lost motion housing distalfrom the actuator piston and the side of the lost motion housingproximal to the actuator piston. Still further, the means for securingthe lost motion housing may comprise a boss extending from the lostmotion housing collar and a bolt extending from the boss into an enginecomponent. Still further, the means for securing the lost motion housingmay comprise a flange extending from the lost motion housing proximal tothe actuator piston and a bolt extending from said flange into an enginecomponent. Still further, the system may further comprise a solenoidvalve adapted to control the supply of hydraulic fluid to said hydraulicfluid supply passage.

It is to be understood that both the foregoing general description andthe following detailed description are exemplary and explanatory only,and are not restrictive of the invention as claimed. The accompanyingdrawings, which are incorporated herein by reference, and whichconstitute a part of this specification, illustrate certain embodimentsof the invention and, together with the detailed description, serve toexplain the principles of the present invention.

BRIEF DESCRIPTION OF THE DRAWINGS

In order to assist the understanding of this invention, reference willnow be made to the appended drawings, in which like reference charactersrefer to like elements. The drawings are exemplary only, and should notbe construed as limiting the invention.

FIG. 1 is a pictorial view of an engine brake system having anarticulated rocker arm and a rocker shaft mounted housing for master andslave pistons constructed in accordance with a first embodiment of thepresent invention and disposed in an internal combustion engine.

FIG. 2 is an overhead exploded pictorial view of an engine brake systemhaving an articulated rocker arm, rocker shaft mounted housing, and arocker arm return spring in accordance with the first embodiment of thepresent invention.

FIG. 3 is an overhead exploded pictorial view of the underside of theengine brake system shown in FIG. 2 as arranged in accordance with thefirst embodiment of the present invention.

FIG. 4 is a cross-sectional side view of a rocker shaft mounted housingof FIGS. 2 and 3 which shows the master and slave pistons arranged inaccordance with the first embodiment of the present invention.

FIG. 5 is a second cross-sectional side view of the rocker shaft mountedhousing of FIGS. 2 and 3 which shows the control valve in hydrauliccommunication with the rocker shaft and the master and slave pistons asarranged in accordance with the first embodiment of the presentinvention.

FIG. 6 is a cross-sectional front view of the rocker shaft mountedhousing of FIGS. 2 and 3 showing the control valve and the slave pistonas arranged in accordance with the first embodiment of the presentinvention.

FIG. 7 is a cross-sectional side view of the engine brake system ofFIGS. 2 and 3 showing the articulated rocker arm, rocker shaft mountedhousing, and cam lobe as arranged in accordance with the firstembodiment of the present invention when the engine brake system isturned off.

FIG. 8 is a cross-sectional side view of the engine brake system ofFIGS. 2 and 3 showing the articulated rocker arm, rocker shaft mountedhousing, and cam lobe as arranged in accordance with the firstembodiment of the present invention when the engine brake system isturned on and rocker arm is contacting the cam base circle.

FIG. 9 is a cross-sectional side view of the engine brake system ofFIGS. 2 and 3 showing the articulated rocker arm, rocker shaft mountedhousing, and cam lobe as arranged in accordance with the firstembodiment of the present invention when the engine brake system isturned on and the rocker arm is contacting the cam compression-releasebump.

FIG. 10 is a cross-sectional side view of an engine brake system showingthe articulated rocker arm, rocker shaft mounted housing, and cam lobeas arranged in accordance with a second embodiment of the presentinvention when the engine brake system is turned off.

FIG. 11 is an exploded pictorial view of an engine brake system havingan articulated rocker arm, rocker shaft mounted housing, and a rockerarm return spring in accordance with the second embodiment of thepresent invention.

FIG. 12 is a cross-sectional side view of the engine brake system ofFIGS. 2 and 3 showing the oil passage schematic between the engine oilsupply passage, solenoid valve and rocker shaft.

FIG. 13 is an overhead pictorial view of a valve actuation system thatmay be used for bleeder braking in particular, having a rocker shaftmounted housing in accordance with a second embodiment of the presentinvention.

FIG. 14 is a pictorial view of the underside of the valve actuationsystem shown in FIG. 13 as arranged in accordance with the secondembodiment of the present invention.

FIG. 15 is a cross-sectional side view of a rocker shaft mounted housingof FIGS. 13 and 14 which shows an alternative or additional flange forsecuring the rocker shaft mounted housing in a fixed position inaccordance with an alternative embodiment of the present invention.

FIG. 16 is a second cross-sectional side view of the rocker shaftmounted housing of FIGS. 13 and 14 which shows the control valve inhydraulic communication with the rocker shaft and the actuator piston asarranged in accordance with the second embodiment of the presentinvention.

FIG. 17 is a cross-sectional front view of the rocker shaft mountedhousing of FIGS. 13 and 14 showing the control valve and the actuatorpiston as arranged in accordance with the second embodiment of thepresent invention.

FIG. 18 is a cross-sectional side view of the valve actuation system ofFIGS. 13 and 14 showing the rocker shaft mounted housing and actuatorpiston as arranged in accordance with the second embodiment of thepresent invention when the actuator piston is separated by a lash spacefrom the sliding pin/engine valve.

FIG. 19 is a cross-sectional side view of the valve actuation system ofFIGS. 13 and 14 showing the rocker shaft mounted housing and actuatorpiston as arranged in accordance with the second embodiment of thepresent invention when the system is turned on and the actuator pistonhas actuated the engine valve.

FIG. 20 is a cross-sectional side view of the valve actuation system ofFIGS. 13 and 14 illustrating control of hydraulic fluid supply by asolenoid valve.

FIG. 21 is a cross-sectional side view of a valve bridge disposedbetween an actuator piston and an engine valve in accordance with analternative embodiment of the present invention.

FIG. 22 is a cross-sectional view of an alternative actuator piston inaccordance with an alternative embodiment of the present invention.

DETAILED DESCRIPTION OF EMBODIMENTS OF THE INVENTION

Reference will now be made in detail to a first embodiment of thepresent invention, an example of which is illustrated in theaccompanying drawings. With reference to FIG. 1, a system 50 foractuating engine valves arranged in accordance with a first embodimentof the present invention is shown. FIGS. 2-9 show different views of thesystem shown in FIG. 1 and/or its components. The system 50 may includea cam 100, an articulated half rocker arm 200, a brake housing 300, arocker shaft 400, and a solenoid valve 500. The rocker arm 200 may bebiased away from (or alternatively towards) the cam 100 by a returnspring 210 (see also FIG. 11). The brake housing may be secured inposition by a anti-rotation bolt 310.

With reference to FIGS. 2 and 3, the rocker arm 200 may further includea cam roller 220, a lug 230, and a central collar 240. The rocker armreturn spring 210 may bias the rocker arm 200 towards the brake housing300 such that the lug 230 contacts the master piston 340. The brakehousing 300 may further include an anti-rotation bolt boss 312, acontrol valve 320, a master piston 340, a slave piston 350 and rockershaft collars 360 and 362. A slave piston return spring 352 may bias theslave piston 350 up into a slave piston bore formed in the brake housing300.

With reference to FIG. 4, the rocker shaft collars 360 and 362 of thebrake housing 300 may be mounted on the rocker shaft 400. The brakehousing may be secured in a fixed position relative to the rocker shaft400 by the anti-rotation bolt 310 (not shown). The brake housing 300 mayinclude a master piston 340 slidably disposed in a master piston bore302 and a slave piston 350 slidably disposed in a slave piston bore 304.A master-slave hydraulic fluid passage 306 may extend between the masterpiston bore 302 and the slave piston bore 304. The slave piston returnspring 352 may bias the slave piston 350 upward and against a slavepiston lash adjustment screw 354 which extends into the slave pistonbore 304. The rocker shaft 400 may include a first hydraulic passage 410adapted to provide lower pressure hydraulic fluid to the rocker arm 200(not shown in FIG. 4) for lubrication purposes. The rocker shaft 400 mayalso include a second hydraulic passage 420, the purpose of which isexplained in connection with FIG. 5.

With reference to FIG. 5, adjacent to the slave piston 350 (shown inFIG. 4) the brake housing 300 may further include control valve 320. Thecontrol valve 320 may fill the master and slave bores with hydraulicfluid when low pressure hydraulic fluid is supplied to the lower portionof the control valve via a supply passage 308. A connection hydraulicpassage 422 provided in the rocker shaft 400 may extend between thesecond hydraulic passage 420 and the supply passage 308 provided in thebrake housing 300. As a result, hydraulic fluid may be supplied to thecontrol valve, and the master and slave bores, by the selective supplyof low pressure hydraulic fluid in the second hydraulic passage 420.

A front cross-sectional view of the brake housing 300 is shown in FIG.6. With reference to FIG. 6, the control valve 320 is shown in a “brakeoff” position during which the control valve body 322 is biased into itslower most position by the control valve spring 326. When the brake isturned on, hydraulic fluid from the second hydraulic passage 420 in therocker shaft 400 (shown in FIG. 5) may be supplied to the lower portionof the control valve body 322. The supply of hydraulic fluid may causethe control valve body 322 to move upward until the annular openingprovided in the mid-portion of the control valve body registers with theslave bore supply passage 309. The hydraulic fluid pressure applied tothe lower portion of the control valve 320 may be sufficient to push thecheck valve 324 open so that hydraulic fluid flows into the slave pistonbore 304 via the slave bore supply passage 309. With renewed referenceto FIG. 4, the hydraulic fluid may further flow from the slave pistonbore 304 through the master-slave hydraulic fluid passage 306 into themaster piston bore 302. While the brake is in a “brake on” position,hydraulic fluid may be supplied freely to the master-slave pistoncircuit by the control valve 320, while the check valve 324 within thecontrol valve prevents the reverse flow of fluid. As a result, themaster-slave hydraulic circuit in the brake housing 300 may experiencehigh hydraulic fluid pressures without substantial back flow ofhydraulic fluid.

The brake may be returned to the “brake off” position shown in FIG. 6 byreducing the hydraulic fluid pressure, preferably by evacuating thehydraulic fluid, applied to the lower portion of the control valve 320.When this happens, the control valve body 322 may slide downward untilthe slave bore supply passage 309 is exposed to the control valve bore328, thereby allowing the hydraulic fluid in the master-slave hydrauliccircuit to escape. The selective supply of hydraulic fluid to thecontrol valve 320 may be controlled by the solenoid 500 shown in FIG. 1.Alternative placements of the solenoid 500 are considered within thescope of the present invention.

The arrangement of the various elements of the system 50 when the enginebrake is in a “brake off” position is shown in FIG. 7. With reference toFIG. 7, the cam lobe 100 is illustrated as having two valve actuationbumps. A first cam bump 102 may provide a compression-release valveactuation event and a second cam bump 104 may provide a brake gasrecirculation (BGR) valve actuation event. Alternative cam lobes withmore, less, or different cam bumps are contemplated as being within thescope of the present invention.

The system 50 is positioned adjacent to an engine valve, such as anexhaust valve 600. The system 50 may actuate the exhaust valve 600through a sliding pin 620 that extends through a valve bridge 610. Useof such a sliding pin and valve bridge arrangement may permit a separatevalve actuation system to actuate multiple engine valves for positivepower operation and a single engine valve 600 for non-positive poweroperation, such as engine braking.

With continued reference to FIG. 7, when the brake is in a “brake off”position, hydraulic fluid pressure in the second hydraulic passage 420is reduced or eliminated. As a result, there is no hydraulic fluidpressure maintained in the master-slave hydraulic fluid circuitconnecting the master piston 340 and the slave piston 350. Accordingly,the bias of the slave piston return spring 352 may be sufficient to pushthe slave piston 350 all the way into the slave piston bore against thelash adjustment screw 354. Furthermore, the bias of the rocker armreturn spring 210 may be sufficient to rotate the rocker arm 200 suchthat the rocker arm lug 230 pushes the master piston 340 all the wayinto the master piston bore. The rotation of the rocker arm 200 in thismanner may create a lash space 106 between the cam roller 220 and thecam lobe 100. The lash space 106 may be designed to have a magnitude xthat is as great or greater than the height of the cam bumps 102 and104. Thus, when the system 50 is in a “brake off” position, the cambumps 102 and 104 may not have any effect on the rocker arm 200 or themaster and slave pistons 340 and 350.

The arrangement of the various elements of the system 50 when the enginebrake is in a “brake on” position is shown in FIG. 8. With reference toFIG. 8, when the brake is turned “on,” hydraulic fluid is suppliedthrough the second hydraulic passage 420 to the control valve 320 (notshown) and the master-piston hydraulic circuit in the brake housing.When the cam lobe 100 is at base circle, as shown in FIG. 8, thehydraulic fluid pressure in the master-slave hydraulic fluid circuitconnecting the master piston 340 and the slave piston 350 may push themaster piston 340 out of its bore, overcoming the bias of the rocker armreturn spring 210 and rotating the rocker arm 200 backwards until thecam roller 220 contacts the cam lobe 100. As a result, the lash space106 may be eliminated. At this time (cam lobe at base circle), thehydraulic pressure in the master-slave hydraulic circuit is notsufficient, however, overcome the bias of the slave piston return spring352 and push the slave piston 350 out of the slave piston bore.

With reference to FIG. 9, when the cam roller 220 encounters the cambump 102 (and 104), the rocker arm 200 is rotated slightly clockwise.Rotation of the rocker arm 200 may push the master piston 340 into themaster piston bore thereby displacing hydraulic fluid through themaster-slave hydraulic fluid passage 306 and into the slave piston bore.As a result, the bias of the slave piston return spring 352 is overcomeand the slave piston 350 may be displaced downward against the slidingpin 620, which in turn, may actuate the exhaust valve 600 for acompression-release event or some alternative valve actuation event.

An alternative embodiment of the present invention is shown in FIGS. 10and 11. With reference to FIGS. 10 and 11, the rocker arm return spring210 may be provided in the form of a coil spring as opposed to amouse-trap type spring. Furthermore, the return spring 210 may extendbetween an overhead element 212 and a rear portion of the rocker arm 200such that the rocker arm is biased into continual contact with the camlobe 100 when the system is in a “brake off” position, as shown in FIG.10. As a result, instead of creating a lash space between the cam lobe100 and the cam roller 220 when the brake is off, a lash space 202 maybe created between the rocker arm lug 230 and the master piston 340.

With reference to FIG. 12, the communication between an engine oilsupply passage 430 and the first and second hydraulic passages 410 and420 are shown. The solenoid 500 may be disposed between the engine oilsupply passage 430 and the rocker shaft 400.

With reference to FIGS. 13 and 14, in a second embodiment of the presentinvention, the rocker arm and master piston may be eliminated. The valveactuation system housing 1300 may include an anti-rotation bolt boss1312, a control valve 1320, an actuator piston 1350 and rocker shaftcollars 1360 and 1362. The rocker shaft collars may surround the rockershaft providing a means for securely fixing the housing 1300 in a fixedand compact position relative to the engine valves to be actuated.

With reference to FIG. 15, the rocker shaft collars 1360 and 1362 of thehousing 1300 may be mounted on the rocker shaft 1400. The housing may besecured in a fixed position relative to the rocker shaft 1400 by a firstanti-rotation bolt 1310 (not shown) that extends through theanti-rotation bolt boss 1312 and/or by a second anti-rotation bolt 1314that extends through an anti-rotation flange 1316. The anti-rotationboss 1312 may be provided distal from the actuator piston 1350 and theanti-rotation flange 1316 may be provided proximal to the actuatorpiston. The housing 1300 may include an actuator piston 1350 slidablydisposed in an actuator piston bore 1304. An internal hydraulic circuitmay include passage 1306 and passage 1308 (shown in FIG. 16). Anactuator piston lash adjustment screw 1354 may extend into the actuatorpiston bore 1304 and provide an upper stop against which the actuatorpiston 1350 may seat. The rocker shaft 1400 may include a hydraulicfluid supply passage 1420, the purpose of which is explained inconnection with FIG. 16.

With reference to FIG. 16, adjacent to the actuator piston 1350 (shownin FIG. 15) the housing 1300 may further include a control valve 1320.The control valve 1320 may fill the passage 1306 of the internalhydraulic circuit with hydraulic fluid when low pressure hydraulic fluidis supplied to the lower portion of the control valve via a passage 1308of the internal hydraulic circuit. A connection hydraulic passage 1422provided in the rocker shaft 1400 may extend between the hydraulic fluidsupply passage 1420 and the passage 1308 provided in the housing 1300.As a result, hydraulic fluid may be supplied to the control valve andthe actuator piston bores by the selective supply of low pressurehydraulic fluid in the hydraulic fluid supply passage 1420.

A front cross-sectional view of the system is shown in FIG. 17. Withreference to FIG. 17, the control valve 1320 is shown in a “actuatoroff” position during which the control valve body 1322 is biased intoits lower most position by the control valve spring 1326. When thesystem is turned on, hydraulic fluid from the hydraulic fluid supplypassage 1420 in the rocker shaft 1400 (shown in FIG. 16) may be suppliedto the lower portion of the control valve body 1322. The supply ofhydraulic fluid may cause the control valve body 1322 to move upwarduntil the annular opening provided in the mid-portion of the controlvalve body registers with the passage 1306. The hydraulic fluid pressureapplied to the lower portion of the control valve 1320 may be sufficientto push the check valve 1324 open so that hydraulic fluid flows into theactuator piston bore 1304 via the passage 1306. While the system is inan “actuator on” position, hydraulic fluid may be supplied freely to theinternal hydraulic circuit by the control valve 1320, while the checkvalve 1324 within the control valve prevents the reverse flow of fluid.As a result, the internal hydraulic circuit in the housing 1300 mayexperience high hydraulic fluid pressures without substantial back flowof hydraulic fluid.

The system may be returned to the “actuator off” position shown in FIG.17 by reducing the hydraulic fluid pressure in the hydraulic fluidsupply passage 1420, and preferably by evacuating the hydraulic fluidapplied to the lower portion of the control valve 1320. When thishappens, the control valve body 1322 may slide downward until thepassage 1306 is exposed to the control valve bore 1328, thereby allowingthe hydraulic fluid in the internal hydraulic circuit to escape. Theselective supply of hydraulic fluid to the control valve 1320 may becontrolled by the solenoid 1500 shown in FIG. 20. Alternative placementsof the solenoid 1500 are considered within the scope of the presentinvention.

The arrangement of the various elements of the system when the enginevalve actuator is in an “actuator off” position is shown in FIG. 18.With reference to FIG. 18, the system is positioned adjacent to anengine valve, such as an exhaust valve 1600. The system may actuate theexhaust valve 1600 through a sliding pin 1620 that extends through avalve bridge 1610. Use of such a sliding pin and valve bridgearrangement may permit a separate valve actuation system to actuatemultiple engine valves for positive power operation and a single enginevalve 1600 for non-positive power operation, such as engine braking.With continued reference to FIG. 18, when the system is in an “actuatoroff” position, hydraulic fluid pressure in the hydraulic fluid supplypassage 1420 is reduced or eliminated. As a result, there is nohydraulic fluid pressure maintained in the internal hydraulic fluidcircuit connected to the actuator piston 1350. As a result, the actuatorpiston 1350 may rest against but not actuate the sliding pin 1620. Thus,when the system is in an “actuator off” position, the actuator pistonmay not provide any valve actuation motion to the engine valve.

The arrangement of the various elements of the system when it is in an“actuator on” position is shown in FIG. 19. With reference to FIG. 19,when the system is turned “on,” hydraulic fluid is supplied through thehydraulic passage 1420 to the control valve 1320 (not shown). Hydraulicfluid pressure in the passage 1306 may push the actuator piston 1350 outof its bore so that if it is not already, it does contact the slidingpin 1620. At this time the hydraulic pressure in the internal hydrauliccircuit may not be sufficient, however, to overcome the bias of theengine valve 1600 spring 1602. When the valve bridge 1610 is moveddownward for main exhaust valve actuation event, for example, the lowpressure hydraulic fluid in the actuator piston bore 1304 may push theactuator piston 1350 and the sliding pin 1620 downward so that theyfollow the valve bridge until the actuator piston reaches its maximumdownward displacement. As the valve bridge 1610 returns upward at theconclusion of the main exhaust event, the hydraulic fluid in the passage1306 may become highly pressurized so that the actuator piston 1350holds the exhaust valve 1600 open for an engine valve event, such as ableeder braking event. The actuator piston 1350 may continue to hold theexhaust valve 1600 open until the control valve 1320 releases thehydraulic fluid pressure in the passage 1306. It is appreciated that thevalve actuation system may be used for intake and auxiliary engine valveactuation in addition to exhaust valve actuation.

With reference to FIG. 20, the communication between an engine hydraulicfluid supply passage 1430 and the hydraulic fluid supply passage 1420 isshown. The solenoid valve 1500 may be disposed between the enginehydraulic fluid supply passage 1430 and the hydraulic fluid supplypassage 1420 in the rocker shaft 1400. The solenoid valve 1500 may beprovided adjacent to the rocker shaft mounted engine brake system on,for example, a rocker shaft pedestal.

With reference to FIG. 21, in an alternative embodiment of the systemshown in FIGS. 13-20, the actuator piston 1350 may act directly on anengine valve 1600 or on an engine valve bridge 1610 instead of acting ona sliding pin.

With reference to FIG. 22, in another alternative embodiment of thesystem shown in FIGS. 13-21, the solid actuator piston 1350 may bereplaced with an auto-lashing actuator piston 1352. The auto-lashingpiston 1352 may include an actuator piston with a hollow interior whichreceives an adjustable depth lash adjustment screw-plunger 1353, spring1355, and retaining collar 1357. The adjustable depth lash adjustmentscrew-plunger may be partially disposed in the hollow interior of theactuator piston 1352 and extend out of the top of the actuator pistonbore 1304. The adjustable depth lash adjustment screw-plunger 1353 mayhave a lower plunger end and the retaining collar 1357 may be disposedin the hollow interior of the actuator piston 1352 above the lowerplunger end. The spring 1355 may be disposed between the retainingcollar 1357 and the lower plunger end. The auto-lashing actuator piston1352 may be maintained out of contact with sliding pin 1620 (as shown inFIG. 18) when the system is in an “actuator off” position.

It will be apparent to those skilled in the art that variations andmodifications of the present invention can be made without departingfrom the scope or spirit of the invention.

1. A system for actuating an engine valve comprising: a rocker shafthaving a hydraulic fluid supply passage; a lost motion housing having acollar surrounding the rocker shaft, an actuator piston bore, and aninternal hydraulic circuit extending from the actuator piston bore tothe hydraulic fluid supply passage; means for securing the lost motionhousing in a fixed position relative to the rocker shaft; and anactuator piston slidably disposed in the actuator piston bore.
 2. Thesystem of claim 1 wherein the hydraulic fluid supply passage extendsinternally through the rocker shaft.
 3. The system of claim 1 whereinthe lost motion housing has two collars surrounding the rocker shaft. 4.The system of claim 3 further comprising: a control valve bore providedin the lost motion housing, said control valve bore communicating withthe internal hydraulic circuit; and a control valve disposed in thecontrol valve bore.
 5. The system of claim 4 further comprising a checkvalve disposed in the control valve.
 6. The system of claim 5 whereinthe means for securing is provided on a side of the lost motion housingwhich is distal from the actuator piston.
 7. The system of claim 5wherein the means for securing is provided on a side of the lost motionhousing which is proximal to the actuator piston.
 8. The system of claim5 wherein the means for securing is provided on both a side of the lostmotion housing distal from the actuator piston and a side of the lostmotion housing proximal to the actuator piston.
 9. The system of claim 6wherein the means for securing the lost motion housing comprises a bossextending from said lost motion housing collar and a bolt extending fromsaid boss into an engine component.
 10. The system of claim 7 whereinthe means for securing the lost motion housing comprises a flangeextending from said lost motion housing proximal to the actuator pistonand a bolt extending from said flange into an engine component.
 11. Thesystem of claim 1 further comprising: a control valve bore provided inthe lost motion housing, said control valve bore communicating with theinternal hydraulic circuit; and a control valve disposed in the controlvalve bore.
 12. The system of claim 11 further comprising a check valvedisposed in the control valve.
 13. The system of claim 1 wherein themeans for securing is provided on a side of the lost motion housingwhich is distal from the actuator piston.
 14. The system of claim 1wherein the means for securing is provided on a side of the lost motionhousing which is proximal to the actuator piston.
 15. The system ofclaim 1 wherein the means for securing is provided on both a side of thelost motion housing distal from the actuator piston and a side of thelost motion housing proximal to the actuator piston.
 16. The system ofclaim 1 further comprising a solenoid valve adapted to control thesupply of hydraulic fluid to said hydraulic fluid supply passage. 17.The system of claim 1 wherein the actuator piston further comprises: ahollow interior; an adjustable depth lash adjustment screw-plungerpartially disposed in said hollow interior and extending out of the topof the actuator piston bore, said screw-plunger having a lower plungerend; a retaining collar disposed in said hollow interior above saidlower plunger end; and a spring disposed between the retaining collarand the lower plunger end.